One-way self-alining torque unit

ABSTRACT

A one-way, self-alining torque unit well suited for heavy duty on a vertical shaft subject to misalinement with respect to coacting torque applying structure. The unit comprises a one-way torque coupling and an alinement coupling integrated together for mounting on a vertical shaft and providing for compensation for misalinement of the shaft with reference to coacting structure which applies torque to the shaft in only one direction through the assembly. Working parts of the alinement coupling and underlying working parts of the torque coupling are continuously bathed in flowing lubricant that descends through a succession of comating working parts all to the end that the unit will operate reliably for many years in locations where access for service is impractical. A reversible cam ring in the unit permits adaption of the unit to transmit torque to the shaft in either direction without structural modification of components of the unit. Interfitting toothed rings accommodate misalinement of the shaft and minimize the overall length of the unit.

[451 Apr. 18, W72

spect to prises a oneg integrated providing for ng parts of the ng partsof the flowing lubricant ing working parts bly for many years practical.A reversiunit. Interfitting toothed rings accommodate misalinement ofthe shaft and minimize the overall length of the unit QUE 3,236,3372/1966 Marland 8t UNIT Primary Examiner-George E. A. Halvosa [72]Inventors: Joseph A. Marland, Hmsdale; Charles W. Ammey }3urmeister, p li g Hamby Hill, La Grange, both of Ill.

Assignee: Marland One-Way Clutch Co., Inc., La [57] ABSTRACT Grange,Ill. A one-way, self-alining torque unit well suited for heavy dutyFiled. Sept. 4 1970 on a vertical shaft subject to misalinement with recoacting torque applying structure. The unit com Appl. No.: 69,584 waytorque coupling and an alinement couplin together for mounting on avertical shaft and Related Application Data compensation formisalinement of the shaft with reference to [63] continuatiommpart ofSen 827,400 May 23 coacting structure which applies torque to the shaftin only 1969, which is a continuation-in-part of Ser. No. 9 dlrecnonthfough the assemPly- 737 965 June 18 1968 abandoned alinement couplingand underlying worki torque coupling are continuously bathed in188/8234, 192/45 that descends through a succession of comat Int. Cl.63/00 f to the end that the f {eha 188/828 8284, 264 B; 1n locationswhere access for service is rm 192/45 ble cam ring in the unit permitsadaption of the unit to transmit torque to the shaft in either directionwithout structural References Cited modification of components of theUNITED STATES PATENTS 8/1961 Marland.............................188/8284 12 Claims, 12 Drawing FiguresUnited States Patent Marland et al.

[54] ONE-WAY SELF-ALINING TOR [58]FieldofSearch..........................

PATENTEBAPR 18 I972 3.656591 SHEET 2 BF 7 Invento rs Jose A .MarlandChar 8' W. #511 PATENTEDAPR 18 m2 656. 591 SHEET 3 UF 7 Inventors JosephA.Marland Charles W. J'HH @WFM 8271M :H-HornEgAS PATENTEDAPRmmIZ2,655,591

' sum u CF 7 Inventors Joseph A.Marland Charles W 71''! a cswmpum & W

aH-lrornee s ONE-WAY SELF-ALINING TORQUE UNIT This application is acontinuation-in-part of copending application Ser. No. 827,400 filed May23, 1969, which in turn is a continuation-in-part of application Ser.No. 737,965, filed June 18, 1968, and now abandoned.

DISCLOSURE This invention relates to one-way torque couplings forrotatable shafts, and is concerned particularly with the control andoperation by such couplings of vertical shafts subject to misalinementand located in environments where access for service is impractical.

One-way torque couplings are recognized mechanisms for limiting rotationof a rotatable shaft to one rotational direction, as clearly indicatedby U.S. Pat. No. 2,865,474 of one of the present inventors, Mr. JosephA. Marland, entitled ONE-WAY AUTOMATIC BACKSTOPS, and by Mr. MarlandsUS. Pat. No. 3,247,935 entitled ONE-WAY BRAKE ASSEMBLY AND SEAL MEANSTHEREFOR. These patents disclose backstops in which a rotatable shaft ismechanically mounted on the inner race of a one-way coupling, the outerrace of the one-way coupling being connected to a stationary structureby means of a beam extending normally from the axis of the shaft. Thebeam is affixed at one end to the structure and at the other end to theouter race of the coupling. The outwardly extending beam requiressubstantial lateral space.

One object of the invention is to provide, for applying torque to ashaft in one direction only, a one-way torque unit having a new andimproved construction which minimizes the lateral size of the unit whileat the same time providing an inherent capability for accommodatingmisalinement of the shaft in a manner which does not subject the unit towear or strain with the consequence that an extremely long, troublefreeservice life is obtained.

A further object is to provide a one-way torque unit of the characterrecited that is especially well adapted for use on a vertical shaft insuch manner that the unit is supported largely on the vertical shaftwith consequent determination of the axial positions of major componentsof the unit, the unit comprising a one-way coupling adapted for supporton a shaft and integrated with an alinement coupling supported on theone way coupling and functioning at once to sustain the torque reactionof the shaft on the one-way coupling and to accommodate misalinement ofthe shaft.

A further object is to provide a one-way, self-alining torque unit, asrecited, having an improved construction which enables the unit tooperate dependably in continuous use over a very long service life thatmay extend literally for decades without repairs or service except forthe supplying of lubricant which may be pumped into the unit.

A further object is to provide a one-way, self-alining torque unit ofthe character recited having an improved and highly advantageousconstruction which facilitates support of the unit on a vertical shaftwhile at the same time utilizing a cascading flow of oil to a maximizedadvantage in assuring most advantageous lubrication of working partscomating on a plurality of levels in the unit.

Another object is to provide a one-way, self-alining torque unit asrecited in which concentricity of major components of a one-way torqueapplying mechanism in the unit is main tained in an advantageous manner.

Another object is to provide a one-way, self-alining torque unit asrecited in which alinement of an annular series of torque transmittingrollers with respect to inner and outer coacting races is maintained toadvantage by a cage joumalled on antifriction bearings.

Another object is to provide one-way, seIf-alining torque unit asrecited which can be adapted, through assembly, without structuralmodification of its component elements to transmit torque to a coactingshaft in either desired direction.

Another object is to provide a one-way, self-alining torque unit asrecited which can function positively to preclude reverse rotation ofthe shaft while at the same time providing for driving of the shaftthrough the unit in the normal direction of shaft rotation.

A further object is to provide a one-way, self-alining torque unithaving an improved construction which accomplishes the foregoing objectswhile at the same time minimizing the length of the unit withoutexpanding significantly the transverse overall dimensions of the unit.

A further object is to provide an improved one-way, selfalining torqueunit according to the previous objects having an improved constructionwhich materially shortens the unit while at the same time providing mosteffective lubrication for coacting working surfaces on componentelements of the unit.

Other objects and advantages will appear from the following descriptionof the exemplary embodiments of the invention illustrated in thedrawings in which:

FIG. 1 is a vertical sectional view showing in solid lines a one-waytorque unit constructed in accordance with the invention andillustrating in phantom lines a housing to which the unit is anchoredand a vertical turbine shaft to which the unit is attached;

FIG. 2 is a transverse sectional view of the unit taken along the line2-2 of FIG. 1;

FIG. 3 is a fragmentary transverse sectional view taken with referenceto the line 33 of FIG. 1;

FIG. 4 is a fragmentary sectional view on an enlarged scale taken alongthe line 44 of FIG. 1;

FIG. 5 is a fragmentary sectional view on an enlarged scale taken alongthe line 5-5 of FIG. 4;

FIG. 6 is a vertical sectional view similar to FIG. 1 but illustrating amodified embodiment of the invention;

FIG. 7 is a fragmentary perspective view on an enlarged scale taken withreference to the line 7-7 of FIG. 6;

FIG. 8 is a fragmentary sectional view similar to FIG. 7 but showing theinner race reassembled on its support in a reversed position to transmittorque to the shaft in the opposite direction;

FIG. 8A is a fragmentary sectional view on an enlarged scalecorresponding to the lower right-hand portion of FIG. 6;

FIG. 9 is a perspective view showing in solid lines the inner race andits support in exploded relation to each other and illustrating inphantom lines the position of the race when reversed and assembled ontoits support to adapt the unit to transmit torque in the oppositedirection;

FIG. 10 is a vertical sectional view similar to FIG. 1 but showinganother modified embodiment of the invention; and

FIG. 11 is a fragmentary. transverse sectional view taken along the line1l-ll of FIG. 10.

Referring now to the drawings, the one-way, self-alining torque unit 8forming the first illustrated embodiment of the invention, FIGS. 1 to 5,functions as a backstop mechanism for preventing reverse rotation of acoacting shaft. The unit 8 is anchored to the cover plate 10 of astationary housing and connected to the upper end of a verticallydisposed shaft 12 of an installation, which is to be controlled by thebackstop. The unit 8 comprises a shaft misalinement coupling 16 whichcouples a one-way torque coupling 14 of the unit to the housing coverplate 10. The shaft 12 may be of any vertical shaft, especially arelatively high speed shaft, mounted on any type of installation.

The one-way torque unit 8 serves as a particularly useful backstopmechanism to prevent reverse rotation of one of a plurality ofcentrifugal pumps utilized to deliver a liquid coolant, such as water,to cool a nuclear reactor. An efficient and reliable backstop mechanismis particularly required for such installations because in the event ofmotor shut down or failure of one of the pumps the hydraulic head ofwater from the other pumps would reverse the rotor of the failing orshut down pump and lead to runaway speeds which could result incentrifugal explosion of the motor or the pump rotor. Such a breakdownleads to hazards of possible radioactive contamination from the nuclearreactor. A backstop mechanism of the type disclosed is rugged andreliable and may be left unattended for many years when used with suchnuclear reactor.

The shaft misalinement coupling 16 allows the components of the one-waytorque coupling 14 to adjust concentrically to a true geometric centerof the vertical pump or motor shaft 12, and such adjustment is attainedwhether the shaft 12 is rotating or is static. The coupling 16 includesan upper or first coupler 17 secured to the cover plate 10, andcomprising a centrally located stub shaft 18 having an upper flange 20secured to the cover plate 10 by bolts 22. A geared hub 24 is keyed tothe stub shaft 18 by a key 25 and has a radial gear 26 comprising anannular series of crowned male gear teeth 28, FIGS. 1 and 2.

A lower or second coupler 19 is positioned immediately below the firstcoupler 17, and this second coupler is carried by the one-way coupling14. The second coupler 19 comprises a centrally located body shaft 30having a centrally disposed passage 32 and forming an integral componentof the one-way coupling 14 as will presently appear. A geared hub 34 iskeyed to the shaft 30 by a key 36 and has a radial gear 38 having anannular series of crowned gear teeth 40.

A cylindrical coupler sleeve 42 spans and engages the upper and lowercouplers 17, 19. The sleeve 42 has an upper wall part 44 and a lowerwall part 46 which have respectively circular protruding flanges 47 and48 that are joined by a plurality of bolt and nut assemblies 50. Theupper and lower parts 44, 46 have respectively internal annular gears 52and 54, each of which has straight cut gear teeth.

The common coupler sleeve 42 is supported on the one-way coupling 14 bythrust member or plate 58 which is secured to and seated in a continuousperipheral groove 60 in the inside wall of the common coupler sleeve 16at the junction of the parts 44 and 46. The thrust plate 58 has acentrally located depending thrust button 62 which bears against asmaller thrust plate 64 mounted in an annular groove 67 on the upper endof the shaft 30. The weight of the coupler sleeve 42 is transferred bythe button 62 to the thrust plate 64 and hence to the shaft 30.

The one-way coupling 14 is coupled to the lower coupler 19 ofthealinement coupling 16 through a body portion 66 of the shaft 30 whichextends from the lower coupler 19 to an inner race 70 of the one-waytorque coupling 14. The torque coupling 14 has an outer race 68 whichconcentrically encircles the inner race 70 as shown. Disposed betweenthe inner and outer races 70, 68 is a roller assembly 72.

It will be noted that in the construction described the upper and lowercouplers 17, 19, the common sleeve 42, the shaft 30, and inner race 70are all attached to the stationary cover plate 10 and are stationary.The outer race 68 and its related mechanism rotate with the shaft 12.

Precise alinement of the inner and outer races 70, 68 is assured by acentering spindle 74 mounted on the outer race 68 and journalled withinthe inner race 70. The centering spindle 74 is coaxially disposedrelative to the inner and outer races 70, 68 and to the shaft 12. Theinner race 70 is mounted on a coaxial bearing 76 which has a layer ofbearing material 78 that journals the spindle 74. A drive plate 80 issecured to the centering spindle 74 by screws 82 and is secured to theouter race 68 by screws 86. The rotatable shaft 12 is secured to thedrive plate 80 by bolts (not shown) which extend through alined bores 90in the shaft 12 and drive plate, FIG. 1.

When the one-way torque coupling 14 is in free wheeling operation, theshaft 12, drive plate 80, centering spindle 74, and outer race 68 rotateas a unit. The inner race 70 does not rotate. Movement of the alinementcoupling 16 in the installation described is limited to working of theparts to accommodate misalinement of the shaft 12.

The inner race 70 has a cammed peripheral surface 96, FIGS. 1 and 3.This peripheral surface of the inner race has a plurality of spacedindentations 98 each of which has a low surface or edge 100 and a highsurface or edge 102.

The roller assembly 72 is mounted on the inner race 70 and includes aplurality of rollers 104 which are movable between the low and highsurfaces 100, 102, the rollers 104 moving toward the low surfaces oredges during free wheeling operation. The rollers 104 move toward thehigh surfaces or edges 102 as an incident to incipient reverse rotationof the shaft 12 to become wedged between the inner race 70 and outerrace 68 to lock the shaft against reverse rotation.

The rollers 104 of the roller assembly 72 are caged between two rings106 and 108 having respectively adjoining support rings 110, 112 securedto the sides thereof away from the rollers. The rings 106 and 110 arefastened together by screws 114, FIG. 5, to form a first ring member andthe rings 108 and 112 are secured together to form a second ring memberof the cage. Adjacent rollers 104 are spaced apart by a spacer member115 disposed between each pair of adjacent rollers, each spacer member115 having conforming concave sides confronting the adjacent rollers andbeing secured on the ring members by pins 116 which extend through thespacer members 115.

The roller assembly 72 is spring biased by a pair of springs 120 and 122on opposite sides of the radial axis of the inner race and extendbetween the rings 110 and 112 and the inner race 70, respectively. Thespring 120 is anchored at one end to ring 110 and at the other end tothe inner race 70. In like manner, FIGS. 4 and 5, the other spring 122extends through an elongated slot 125 in the cammed surface 96 in theinner race 70. The slot 125 communicates with a slotted pocket 125a ofsmaller width in the inner race 70 and one end of the spring 122 issecured to the inner race 70 by a screw 126 which passes through thepocket 125a and engages a tapped bore 129 in the body of the inner race70. The other end of the spring 122 is secured in an arcuate slot 131extending into the ring 112. This end of the spring 122 is secured tothe cage ring 112 by a screw 124 which passes through slot 131 into atapped bore 132 in the ring 112. The springs 120, 122 urge the cage inthe direction to move the rollers 104 towards the raised edges 102 ofthe cams and insure early and concurrent engagement of the rollers 104between the inner race 70 and the outer race 68 in response to incipientreverse rotation of the shaft 12.

The roller assembly 72 also includes at least one stop lug 134 disposedin each of the rings 106 and 108, FIG. 4. The stop lug 134 has aninwardly extending portion which extends into slot 142 in the inner race70. Each lug has a tooth portion 148 adapted to abut an adjacent ledge150 on the inner race 70 intervening between the inner and outer edges100, 102 of two adjacent indentations 98 in the inner race. The stoplugs 134 are a part of the rings 106 and 108 and limit the distancewhich the rollers 104 can move toward the inner edges 100 of theindentations 98 to keep the rollers from abutting the inner race 70 atthe raised edges 102 of the adjacent indentations 98 thereby eliminatingfriction.

The cage is also provided with a support ring 136 on the side of theplate 110 away from the rollers 104. The support ring 136 rests on anarcuate shoulder 138 to support the weight of the roller assembly andprevent axial movement.

In addition to the bearing surface formed by the support ring 136 andshoulder 138, the roller cage is supported by an upper ball bearingassembly 150 and a lower ball bearing assembly 152. As best illustratedin FIG. 5, each ball bearing assembly has an outer raceway 154 which issecured to and seated in a groove 156 formed in one of the end membersof the cage. In particular, the outer raceway 154 of ball bearingassembly 152 is seated in adjoining portions of end ring 108 and plate112. Each of the ball bearing assemblies 150, 152 has an inner raceway158 abutting a cylindrical surface of the inner race 70. A plurality ofball bearings 160 are conventionally caged between the raceways 154 and158 of each bearing assembly. As illustrated, the ball bearing assembly150 is similarly secured between end ring 106, plate 110 and inner race70.

The ball bearing assemblies 150 and 152 maintain the roller cage inradial alinement with the inner race 70. Thus, the ball bearingassemblies 150 and 152 prevent radial misalinement fonn causing aportion of the rollers 104 to abut the relatively high-speed metallicsurface of the rotating outer race 68 in free wheeling, which wouldcause wobbling. This construction thus leads to prolonged life of theclutch elements in that physical contact is markedly reduced, duringfree wheeling operation, between the relative stationary elongatedrollers 104 and the inner surface of the outer race 68.

An important feature of the one-way torque unit 8 described is thelubrication system which delivers lubricant to the bearing surfaces ofthe alinement coupling 16 and the underlying one-way torque coupling 14.The lubrication system has a source tank or reservoir 170, FIG. 1, fromwhich liquid lubricant is delivered under pressure by a pump 172 into aline 174 and then to a lubricant entry or port 176 in the stub shaft 18of the uppermost coupler 17. Entry 176 communicates with a plurality oftransverse lubricant passageways 178, and a plurality of downwardlyextending outlet ports 180 allow such drops of lubricant to fall ontothe meshing gears 26 and 38 of the alinement coupling 16. The drops ofliquid lubricant fall between the geared hub 24 and the upper part 44 onthe common coupler sleeve 42.

The thrust member plate 58 receives excess lubricant from the relativelystationary gears 26 and 38 which floods the entire region between theupper wall part 44 and the geared hub 24, and overflows the upper end orlip 183 of the wall part 44. A small aperture 184 in the thrust plate 58allows a few drops of the lubricant to fall on the thrust plate 64. Theplate 64 is provided with a protruding ring 185 which retains a pool oflubricant about the thrust button 62. The lubricant overflowing the ring185 flows into the space 186 between the hub gear 34 and the lower part46 of the common coupler sleeve 42. The aperture 184 is sufficientlysmall in its cross-sectional area so that a sufficient body of lubricantis allowed to pool and flood the meshing gears of the upper coupler.

The lubricant moves through space 186 through opening 188 at the bottomof the common coupler sleeve 42 an then pools in a cup-shaped member oroil collector 190. The oil collector 190 receives lubricant overflowingthe lip 183 of the coupler sleeve 42 from the space between the topcoupler hub 24 and the upper common coupler part 44 and flowing throughchannels 191 formed in the flanges 47 and 48 in parallel relation to theaxis of the coupler sleeve 42. The collector 190 has a bottom wall 192,which is normal to the axis of the spindle 30, and a continuouscylindrical side wall 194 coaxial with the spindle 30 and provided withan inwardly tapering lower end. The lubricant floods the cup-shaped oilcollector 190 and overflows the top edge 196, whereupon it flows downthe wall 194 and drips on the roller assembly 72.

Thereafter the lubricant flows through the roller assembly 72 bygravity, lubricating it and the surfaces of the inner race 70 and outerrace 68, before draining from the outlets 198 and 200 in the drive plate80 and shaft 12, respectively. Such drained lubricant is returned to thereservoir 170 as indicated by dotted line 202, FIG. 1, but it is to beunderstood that an open container below the outlets 200, not shown, mustbe utilized to collect the liquid lubricant since the shaft 12 isrotating at high speed.

The foregoing lubrication sys tem adequately and efficiently lubricatesthe bearing surfaces in the alinement coupling 16, but a furtherlubrication system is provided for delivering lubricant to the one-waytorque coupling 14 and to the bearing surface of the spindle 74 toassure adequate and efficient lubrication thereof.

A conduit, such system flexible metal conduit 204, is connected at oneend, through coupler means, to outlet 206 of one of the transversepassageways 178. The other end of the conduit 204 is connected, throughother coupler means, to an inlet 208 disposed in the body member 66. Theinlet 208 communicates with a circular cavity 210 defined by the bodymember 66 and the confronting surface of the bearing member 76. Thecircular cavity 210 communicates with a plurality of dependingpassageways 209 in the body member, and also communicates with aplurality of upper transverse bearing passageways 211.

Lubricant flowing from the passageways 211 lubricates the surfacebetween the spindle 74 and the layer of bearing material 78. A verticalpassageway 213 communicates with a central circular cavity 215 whichextends through the layer 78 of bearing material and into the body 66,and the passageway 213 communicates with a cavity 212 on the top side ofthe spindle 74. The cavity 212 and passage 32 fill with oil due to theoil pressure between the spindle 74 and the layer 78 of bearingmaterial, thus applying pressure against the upper surface of thespindle 74 and assuring a thick oil film between the bearing surfaces,the spindle 74 and the layer 78. A plurality of lower transversepassageways 217 extend between the vertical passageways 209 and thespindle 74 to convey lubricant from the vertical passageways 209 and thespindle 74 to convey lubricant from the vertical passageways 209 to therotating bearing surface of centering spindle 74. Passageways 209 alsocommunicate with inset vertical passageways 216 to allow lubricant tocontact the horizontal surface 229 of the centering spindle 74, whichsurface must be adequately lubricated since it supports the weight ofthe inner race 70, roller assembly 72, and lower coupler assembly 19.The vertical passageways 209 also communicate with lateral passageways218 which extend to the upper end of the roller cage to convey lubricantto the roller assembly 72. Lubricant flows downward over the rollerassembly 72 and collects in a circular recess 220 disposed about thespindle 74, which also receives lubricant from the bearing surfacesbetween the spindle 74 and layer 78 of bearing material therebymaintaining a pool of lubricant for the horizontal bearing surfacesbetween these elements. The excess lubricant flows out of drain outlets200.

It is to be noted that a plurality of vent apertures 222 are disposed inthe lower wall member 46 of the alinement coupling 16. These ventapertures are to prevent a static air pressure from developing withinthe lower sleeve member 46 which would prevent flooding of the gears 38and 40 with lubricant.

With reference to the modified embodiment of the invention illustratedin FIGS. 6 through 9, component elements which are counterparts of theunit 8 described are identified with the same reference numbers with theaddition of the suffix a. Y

The integrated one-way torque unit 8a forming the modified embodiment ofthe invention referred to is so constructed that it can be-readilyadapted through selective assembly of its components, without structuralmodification of its parts, to transmit torque to the coacting verticalshaft 12a in either direction that is preselected.

In the construction f the unit 8a, the inner race 70a of the one-waytorque coupling 14a is fabricated as an independent annular part, asshown in FIGS. 6 through 9, separate from the coupler 19a that is acommon integral component of both the one-way torque coupling 14a andthe alinement coupling 16a.

The outer periphery of the separately formed inner race 70a, which has agenerally cylindrical annular shape over all, is fashioned, between itsopposite ends, to define a cammed peripheral surface 96a shapedsimilarly to the cammed peripheral surface 96 on the inner race 70 ofthe previously described unit 8.

The lower end of the bottom portion 660 of the common coupler element19a is externally shaped to define a cylindrical race support 230dimensioned to fit into a cylindrical axial bore 232 defined within theseparately formed race 70a.

At its opposite ends, FIGS. 1 and 9, the separately formed race 70a isshaped outwardly of the cammed peripheral surface 96 to define twonarrow grooves 234, 236 opening outwardly to receive selectively aretaining ring 238 for supporting the roller assembly 72a, as will bepresently described.

The annular race 70a is designed to be turned end for end and fittedonto the cylindrical support 230 on the coupler part 66a so that eitherend of the race 70a abuts against an annular shoulder 240 formed on thecoupler part 66a at the alinement coupling end of the cylindricalsupport element 230.

The race 70a is precluded from turning on its cylindrical support 230 byone or more axial keys 242 fitted into alined keyways 244, 246 formed inthe inner periphery of the race 70a and the outer periphery of thecylindrical support 230 as illustrated in FIGS. 7 and 9. The upper endof the assembled race 70a is held in engagement with the annularabutment 240 on the coupler part 66a by a radial annular extension 248on the lower end of the sleeve bearing 76a that fits within the lowerportion of the part 66a and journals the spindle 74a. The sleeve bearing76a is moved into place in the lower end of the part 66a and secured inplace by small screws 250 which extend through the marginal edge of theradial annular extension 248 on the sleeve bearing and are threadedaxially into the lower end of the cylindrical support part 230 for theinner race 70a as shown in FIG. 6. The annular bearing extension 248 issufficiently large in diameter to radially overlap the lower end of therace 70a and hold the race and its driving key or keys 242 against axialdislodgement from their normal positions.

It may be noted here that the radial annular extension 248 on the sleevebearing 76a is covered on its lower side with the layer of bearingmaterial 78a and rests slidably on the generally fiat annular bearingface 229a on the spindle 74 to support the common coupler 19a in themanner described previously in relation to the torque unit 8.

It will be noted with reference to FIGS. 7, 8 and 9 that the slopingroller support surfaces of the indentations 98a forming the cammedperiphery 96a all have a common circumferential orientation in that suchsurfaces slope outward in the same circular direction as will be evidentfrom the previous description of the unit 8. Moreover, it will beappreciated that the direction of orientation of the slope of the rollersupport surfaces of the indentations 98a detennines the direction inwhich the unit will transmit torque to the coacting shaft 12a andconversely the rotary direction in which the unit will sustain, throughthe integrated couplings 14a and 16a, a torque reaction from the shaft12a.

In the unit 8a, provision is made by means of the construction describedfor adapting the unit to transmit torque to the shaft 12 in eitherdirection, which can be predetermined as desired by selectiveorientation of the race 70a as it is assembled onto its generallycylindrical support 230. By turning the race 70a end for end between afirst position illustrated in solid lines in FIG. 9 and a secondposition illustrated in phantom in FIG. 9 and assembling the race ineither one position or the other, the roller engaging surfaces of theindentations 98 may have either the orientation illustrated in FIG. 7 orthe orientation illustrated in FIG. 8 with the consequence that theshaft 12a can be allowed to rotate freely in the particular directiondesired and the unit 8a will function accordingly to sustain a torquereaction of the shaft 120 on the unit in the corresponding reversedirection.

As illustrated best in FIG. 8a, the cage assembly 72a is supported by aring 250 having a vertical leg 252 directly supporting the cage assembly72a and joining at its lower edge a thicker leg 254 extending radiallyinward into overlapping relation to the outer race 256 of a ball bearing258 that is supported by the previously mentioned retaining ring 238releasably fitted into the lower ring support groove 234.

In the event the inner race 70a is assembled in its inverted position toprovide for free rotation of the shaft 12a in the opposite direction,the cage assembly 72a is supported in the same manner, the support ring238 being lodged in this instance in the ring groove 236, FIG. 6, in theopposite end of the race 70a.

Continuous and adequate lubrication of the cage assembly 72a andcoacting working surfaces on the outer race 68a and inner race 70a isassured for either of the two preselected assembly positions of theinner race 70a by means of one or more continuously fed lubricantdischarging fountains 260 positioned as illustrated in FIG. 6 to pourlubricant through the annular space between the upper ends of the innerand outer races 70a, 68a onto the cage assembly 72a.

The fountain 260 is supported in a radial lubricant supply bore 262extending radially through the annular wall of the common coupler part66a into the annular chamber 2100 that is continuously supplied withincoming lubricant through the bore 208a connected with a lubricantsupply fitting 262 which also supplies lubricant to the supply line 204a.

The torque unit 8a not only functions to preclude reverse rotation ofthe shaft 12a in either direction as preselected by the orientation ofthe inner race 70a within the unit, but also provides for power drivingof the shaft 12a through the unit 8a as this may be desirable. Thetransmission of torque through the unit 8a either to drive the shaft 12aor to effect driving by the shaft of structure located at the oppositeend of the unit is provided by extending the spindle 74a upwardlythrough the center of the unit to connect, as shown in FIG. 6, with adrive coupling 264 that connects as illustrated with an auxiliary driveshaft 266.

The spindle 74, elongated to extend upwardly through the unit 8a asdescribed, passes through the central passage 32a in the common coupler19a, which is enlarged to provide clearance around the spindle 74a, andcontinues upwardly through an axial passage 268 formed centrally withinthe upper coupler 170, the end of the spindle 74 connecting with thedrive coupling 264 above the coupler 17a as shown.

Clearance between the upper coupler 17a and the lower coupler 19a foraccommodation of the extended spindle 74a is provided by assemblingbetween the upper and lower components 44a, 46a of the upper couplingsleeve 4211 an annular ring 270 widely spaced radially from the spindle740.

In the unit 8a, the upper coupling sleeve 42a is supported on the oilcollector 190a by means of a resilient ring 272 positioned between thelower edge of the sleeve 42a and the bottom wall 192a of the oilcollector. In this instance, the oil collector bottom wall 1920 isenlarged radially somewhat beyond the sleeve 42a and the cylindricalside wall 194a of the collector is extended upwardly substantially to aflush relation to the upper end of the sleeve 42a with the consequencethat lubricant cascading downwardly from the supply ports a enters thespace between the sleeve 42a and the working parts of the upper coupling16a which operate in a continuously refreshed lubricant bath maintainedaround the working parts of the upper coupling 16a by virtue of thecapability of the upwardly extended oil collector a to contain oil up tothe upper level of the working parts in the upper coupling.

The torque unit 812 illustrated in FIGS. 10 and 11 constitutes anothermodified embodiment of the invention in which component elements whichare counterparts of corresponding components of the torque unitspreviously described are denoted with the same reference numbers butwith the usage of the sufiix b.

Structural features incorporated into the torque unit 8b materiallyreduce the overall axial length of the unit while at the same timepreserving the strength, durability and longevity of the workingcomponents. Thus, the shaft misalinement coupling 16b is compressed inits axial extent so that it is substantially accommodated within theaxial length of the hub 34b which supports the gear 38b integral withthe hub 34b. The hub 34b has a rather substantial length along thesupporting shaft 30b thus providing a steady and most secure support tothe gear hub 34 by the shaft 30b while at the same time facilitatingfixing of the gear hub 34b against rotation relative to the shaft 30b bymeans of a long key 36b, which makes for economical manufacture andassembly of the shaft 30b and gear hub 34b in the construction of thelower coupler 19b.

The external, torque transmitting teeth 40b on the gear hub 34b meshwith an annular series of internal, torque transmitting teeth 300 formedwithin one end of a hollow and generally cylindrical connecting coupleror sleeve 302. The connecting coupler or sleeve 302 extends upwardlyfrom its geared lower end which meshes with the lower external teeth 40bto an upper end of the coupler sleeve 302 that defines an length of thesleeve.

The upper annular series of teeth 304 on the connecting coupler 302 meshwith an annular series of internal, torque transmitting teeth 306 on astationary ring 308 fixed by screws 310 to an overlying mounting plate312 adapted to be anchored to stationary support structure, such forexample as the cover plate 10 illustrated in FIG. 1 and forming theupper coupler 17b.

The connecting coupler sleeve 302 is floatingly supported on an annularseries of helical compression springs 314 underlying the lower end ofthe sleeve 302 as shown in FIG. 1 and held in place by the upper ends ofa corresponding annular series of screws 316 threaded through the flathorizontal bottom wall or floor 192b of the annular oil collector cup190b, the bottom wall l92b providing support to the lower ends of thesprings 314 as shown.

The cylindrical side wall 194b of the oil collector cup 19% extendsupwardly in encircling relation to the intermeshing elements of themisalinement coupling 16b to an upper edge 318, FIG. 10, disposedslightly above the upper extremities of the intermeshing gear teeth 304,306 into substantially flush relation to the upper ends of the generallyconterminous shaft 30b and inner gear hub 34b.

A jet of lubricating oil is continuously introduced into the oil cup190b through an oil inlet orifice 320 formed in the side wall 194b ofthe cup 1901) slightly below the stationary gear ring 308 and fed withoil under pressure through the oil supply conduit 2041; leading from theoil inlet fixture 262b. Circulation of oil within the collector cup l90baround working elements of the misalinement coupling 16b is aided byprovision of a plurality of circumferentially spaced oil circulationbores 322 formed in the coupling sleeve 302 below the upper gear teeth304 as shown in FIG. 1. Oil can flow through the bores or ports 322 intothe annular space 324 intervening between the coupling sleeve 302 andthe upwardly extending gear hub 34b. The space 324 communicates at itslower end with the meshing lower gear teeth 40b and 300 and communicatesat its upper end with the head space 326 intervening between the upperend of the sleeve 302 and the mounting place 312. Any excess oilentering the head space 326 can escape outwardly through a plurality ofradial ports 328 formed in the upper gear ring 308 above the gear teeth306.

A plurality of small drainage openings 330 formed in the bottom 19217 ofthe oil collector cup 19% provide for an outflow of oil from the bottomof the collector cup 19% at a sufficient rate to scavange sediment fromthe bottom of the collector cup so that the working parts of thecoupling 16b remain clean. Excess oil entering the collector cup throughthe orifice 320 circulates around the working parts of the coupling 16bto overflow the upper edge 318 of the collector cup.

Other components of the unit 8b are constructed and operate in the samemanner as counterpart elements of the unit 8a previously described.

The invention is claimed as follows:

1. A one-way backstop for engaging a rotatable shaft to limit the shaftto rotation in one direction comprising, in combination, a stationaryhousing, a first coupler having a first member mounted on the housingand a second member pivotally mounted on the first member, said firstmember comprising a first cylindrical hub secured to the stationaryhousing and protruding therefrom, said first hub having a radial geardisposed thereabout, a second coupler having two pivotally connectedmembers, the second member of the first coupler being one of the membersof the second coupler, the

other member of said second coupler having a second cylindrical hubspaced from the first coupler and having a central axis generallyparallel and approximately alined with the central axis of said firsthub, said central axes of the first and second hubs being disposedgenerally vertical, said second hub having a radial gear disposedthereabout, said second member of the first coupler being a hollowcylindrical sleeve disposed about and adjoining said first and secondhubs, said sleeve having spaced interior radial gears meshed with thegears of said first and second hubs, a one-way torque coupling having afirst race and a second race, said first race being coaxially disposedabout the second race, said torque coupling having a plurality of driveelements disposed between said races, the drive elements transmittingtorque from the first race to the second race for rotational momentsbetween the races in one direction of relative rotation of the races,said drive elements permitting the first and second races to rotatefreely with respect to each other in the other direction of relativerotation of the races, one of said races being secured to the othermember of the second coupler, the other race of the one-way torquecoupling being adapted to be rigidly coupled to the shaft to be limitedto rotation in one direction, a cupshaped lubricant collector secured tosaid second hub below the gear engagement of said second hub with saidsleeve, said collector having a continuous cylindrical side wall coaxialwith the axis of the second hub and having a horizontal upper edgedisposed above the gear of the second hub, and means for maintaining thecollector substantially full of liquid lubricant, thereby maintainingthe gear of the second hub in a pool of lubricant.

2. A one-way backstop for engaging a rotatable shaft to limit the shaftto rotation in one direction comprising the combination of claim 1wherein the first hub is provided with a transverse lubricant passagewayabove the gear of said first hub, said first hub defines a lubricantentry communicating with said transverse lubricant passageway, a sourceof liquid lubricant connected to said lubricant entry in said first hub,and an outlet port in said transverse passageway, said outlet port beingpositioned above and confronting the gear of said first hub and theupper gear of the sleeve so that lubricant falls from said port on themeshed gears of the first hub and sleeve.

3. A one-way backstop for engaging a rotatable shaft to limit the shaftto rotation in one direction comprising the combination of claim 1wherein the sleeve is provided with a flat generally horizontal plateextending within the inner wall thereof between the gears thereof, saidplate carrying a protruding part-spherical button disposed on the lowerside thereof and concentric with the central axis of the first hub, saidbutton resting on a generally horizontal surface on the second hub, andsaid horizontal plate having an aperture confronting said horizontalsurface on the second hub so that lubricant from the gears of the firsthub collecting on the generally horizontal plate flows through theaperture thereof to flood the flat surface on the second hub andlubricate the button and flat surface of the second hub.

4. A one-way backstop for engaging a rotatable shaft to limit the shaftto rotation in one direction comprising the combination of claim 1wherein the cup-shaped collector is disposed above the region of theone-way torque coupling between said inner and outer races thereof,whereby liquid lubricant overflowing the upper edge of the cylindricalwall of said collector drips on the one-way torque coupling.

5. A one-way, self-alining torque unit comprising, in combination, agenerally circular upper coupler having one face adapted for attachmentto a stationary support, said upper coupler having a gear support on theunderside thereof, an upper external gear fixed to said gear support anddefining an annular series of radially projecting crowned gear teeth, alower coupler disposed in underlying generally coaxial relation to saidupper coupler, a lower external gear fixed to said lower coupler anddefining an annular series of radially projecting crowned gear teeth, aconnecting coupler sleeve axially spanning said upper and lower gears inencircling relation thereto, said sleeve having an upper internal gearand a lower internal gear meshing respectively with said upper and lowerexternal gears to transmit torquc therebetween while allowing movementof said lower coupler and said lower external gear thereon in relationto said upper coupler, said upper coupler having thereon a lubricantfountain positioned in overlying relation to said upper external gearand said upper internal gear to direct lubricant downwardly thereonto, asleeve support disc medially positioned axially on said coupler sleeveand extending transversely thereacross in overlying relation to saidlower coupler, said support disc defining on the underside thereof aconvex thrust element supported on the upper end of said lower coupler,said support disc having an aperture medially located therein to directlubricant through the support disc onto said lower coupler adjacent saidthrust element to lubricate the latter and to flow over said lowercoupler onto said lower external gear and said lower internal gear tolubricate the latter, a lubricant retaining cup mounted on said lowercoupler in encircling relation to the latter below said in ternal andexternal lower gears and extending upwardly in encircling spacedrelation to the lower portion of said sleeve to retain lubricant inpooling relation to said lower gears, a first one-way torque couplingrace disposed below said cup and fixed to said lower coupler, a secondone-way torque coupling race disposed in encircling relation to saidfirst race for rotation relative thereto, a roller cage assemblydisposed between said races in coacting relation thereto to transmittorque therebetween in only one rotary direction to preclude rotation ofthe races relative to each other in said one direction while permittingfree relative rotation of the races in the opposite direction, saidraces and said roller cage assembly being positioned to receivelubricant overflowing said lubricant cup, a sleeve bearing supportedwithin said first race in coaxial relation to said lower gear, a spindleconnected with said second race and journalled within said sleevebearing to maintain said races in mutually coaxial relation, means forconnecting said second race nonrotatably with a rotary part, lubricantsupply means connected with said lower coupler for supplying lubricantthereto, and a lubricant fountain connected to receive lubricant fromsaid lower coupler and positioned to pour lubricant onto the cageassembly intervening between said races.

6. A one-way, self-alining torque unit comprising, in combination, anupper coupler adapted to sustain a torque reaction, an upper externalgear fixed to said upper coupler, a lower coupler disposed in underlyinggenerally coaxial relation to said upper coupler, a lower external gearfixed to said lower coupler, a connecting coupler sleeve axiallyspanning said upper and lower gears in encircling relation thereto, saidsleeve having an upper internal gear and a lower internal gear meshingrespectively with said upper and lower external gears to transmit torquetherebetween while allowing movement of said lower coupler and saidlower external gear thereon in relation to said upper coupler, alubricant outlet positioned to flow lubricant onto said upper externaland internal gears, a sleeve support element supporting said couplersleeve on said lower coupler, a lubricant retaining cup mounted on saidlower coupler in encircling relation to the latter below said internaland external lower gears and extending upwardly in encircling spacedrelation to the lower portion of said sleeve to retain lubricant inpooling relation to said lower gears, a first one-way torque couplingrace of annular form defining a circumferential series of roller supportsurfaces sloping outwardly in a common circumferential direction; saidlower coupler including means for supporting said annular race thereonbelow said cup in generally coaxial relation to said gears in either oftwo mounting positions, which positions are turned end for end inrelation to each other so that the common slope of said rollersupporting surfaces is selectively oriented circumferentially in eitherof two circumferential directions; a second one-way coupling raceencircling said first race, an annular series of rollers disposedbetween said races in alinement with said respective surfaces totransmit torque between the races in only one direction predetennined bythe selected orientation in which said inner race is assembled onto saidlower coupler thereby precluding relative rotation of said races in saidone direction while continuously pennitting relative rotation of theraces in the opposite direction, said races and said rollers beingpositioned to receive lubricant overflowing said cup, means forconnecting said second race nonrotatably with a rotary part, and alubricant fountain positioned to flow lubricant into the spaceintervening between said races.

7. A one-way, self-alining torque unit comprising, in combination, anupper coupler adapted to sustain a torque reaction, an upper externalgear fixed to said upper coupler, a lower coupler disposed in underlyinggenerally coaxial relation to said upper coupler, a lower external gearfixed to said lower coupler, a connecting coupler axially spanning saidupper and lower external gears in encircling relation thereto, saidconnecting coupler having an upper internal gear and a lower internalgear meshing respectively with said upper and lower external gears totransmit torque therebetween while allowing movement of said lowercoupler and said lower external gear thereon in relation to said uppercoupler, a lubricant outlet positioned to flow lubricant onto saidgears, a first oneway torque coupling race of annular form defining acircumferential series of roller support surfaces sloping outwardly in acommon circumferential direction; said lower coupler including means forsupporting said annular race thereon in generally coaxial relation tosaid gears in either of two mounting positions, which positions areturned end for end in relation to each other so that the common slope ofsaid roller supporting surfaces is selectively orientedcircumferentially in either of two circumferential directions; a secondone-way coupling race encircling said first race, an annular series ofrollers disposed between said races in alinement with said respectivesurfaces to transmit torque between the races in only one directionpredetermined by the selected orientation in which said inner race isassembled onto said lower coupler thereby precluding relative rotationof said races in said one direction while continuously permittingrelative rotation of the races in the opposite direction, means forconnecting said second race nonrotatably with a rotary part, and alubricant outlet positioned to flow lubricant into the space interveningbetween said races.

8. A one-way, self-alining torque unit comprising, in combination, anupper coupler adapted to sustain a torque reaction, a first annularseries of torque transmitting teeth on said upper coupler, a lowercoupler disposed below said upper coupler, a second annular series oftorque transmitting teeth on said lower coupler, a connecting coupler ofgenerally cylindrical overall form extending axially into axiallyoverlapping relation to said first and second series of teeth on saidupper and lower couplers respectively, said connecting coupler having anupper annular series of torque transmitting teeth and a lower annularseries of torque transmitting teeth meshing respectively with said firstand second annular series of teeth to transmit torque between said upperand lower couplers while allowing movement of said lower couplernonrotatably in relation to said upper coupler, an oil collector cupmounted on said lower coupler in encircling relation to the latter belowsaid connecting coupler and extending upwardly in encircling relation tothe connecting coupler to retain an annular pool of oil in immersingrelation to torque transmitting teeth on the connecting coupler andcoupler teeth meshing therewith, lubricating means including a lubricantoutlet positioned to direct a flow of oil onto meshing torquetransmitting teeth of the aforementioned couplers and into said oilcollector cup to form a pool of oil therein, a first one-way torquecoupling race of generally circular form disposed below said cup andfixed to said lower coupler, a second one-way torque coupling race ofgenerally circular form disposed in encircling relation to said firstrace for rotation relative thereto, one of said races defining anannular series of roller support surfaces sloping toward the other racein a common circumferential direction, an annular series of rollersdisposed between said races in alinement with said respective rollersupport surfaces to transmit torque between the races in only onedirection to preclude rotation of the races relative to each other insaid one direction while permitting free relative rotation of the racesin the opposite direction, a sleeve bearing supported within said secondcoupler in coaxial relation to said first race, a spindle connected withsaid second race and journalled within said bearing to maintain saidraces in mutually coaxial relation, means for connecting said secondrace nonrotatably with a rotary part, lubricating oil supply meansconnected with said lower coupler for supplying lubricating oil thereto,and means on said lower coupler defining a lubricating oil passage fordirecting lubricating oil from said lower coupler onto said rollersintervening between said races.

9. A torque unit according to claim 8 in which said connecting coupleris floatingly supported by a plurality of springs disposed within saidoil collector cup.

10. A torque unit according to claim 8 in which said first annularseries of torque transmitting teeth on said upper coupler are internalteeth meshing with external teeth constituting said upper annular seriesof torque transmitting teeth on said connecting coupler and said secondannular series of torque transmitting teeth on said lower coupler areexternal teeth meshing with internal teeth constituting said lowerannular series of torque transmitting teeth on said connecting coupler.

11. A torque unit according to claim 10 in which said second annularseries of torque transmitting teeth are formed on the lower end portionof a generally cylindrical hub extending upwardly along said lowercoupler in encircling relation thereto for an axial distance which isseveral times greater than the axial extent of the mutually overlappingrelation of said second series of teeth on said lower coupler with saidlower series of teeth on the connecting coupler, a key is recessed intosaid hub and said second coupler in axially extending relation theretoto hold the hub and the second coupler against rotation relative to eachother, and said first annular series of torque transmitting teeth andsaid upper series of teeth on the connecting coupler are locatedsubstantially in encircling relation to the upper end portion of saidhub.

12. A torque unit according to claim 11 in which said oil collector cupextends upwardly into overlapping encircling relation to the mutuallymeshing teeth of said first series and of said upper series on theconnecting coupler to hold an annular pool of oil in immersing relationthereto.

1. A one-way backstop for engaging a rotatable shaft to limit the shaftto rotation in one direction comprising, in combination, a stationaryhousing, a first coupler having a first member mounted on the housingand a second member pivotally mounted on the first member, said firstmember comprising a first cylindrical hub secured to the stationaryhousing and protruding therefrom, said first hub having a radial geardisposeD thereabout, a second coupler having two pivotally connectedmembers, the second member of the first coupler being one of the membersof the second coupler, the other member of said second coupler having asecond cylindrical hub spaced from the first coupler and having acentral axis generally parallel and approximately alined with thecentral axis of said first hub, said central axes of the first andsecond hubs being disposed generally vertical, said second hub having aradial gear disposed thereabout, said second member of the first couplerbeing a hollow cylindrical sleeve disposed about and adjoining saidfirst and second hubs, said sleeve having spaced interior radial gearsmeshed with the gears of said first and second hubs, a one-way torquecoupling having a first race and a second race, said first race beingcoaxially disposed about the second race, said torque coupling having aplurality of drive elements disposed between said races, the driveelements transmitting torque from the first race to the second race forrotational moments between the races in one direction of relativerotation of the races, said drive elements permitting the first andsecond races to rotate freely with respect to each other in the otherdirection of relative rotation of the races, one of said races beingsecured to the other member of the second coupler, the other race of theone-way torque coupling being adapted to be rigidly coupled to the shaftto be limited to rotation in one direction, a cup-shaped lubricantcollector secured to said second hub below the gear engagement of saidsecond hub with said sleeve, said collector having a continuouscylindrical side wall coaxial with the axis of the second hub and havinga horizontal upper edge disposed above the gear of the second hub, andmeans for maintaining the collector substantially full of liquidlubricant, thereby maintaining the gear of the second hub in a pool oflubricant.
 2. A one-way backstop for engaging a rotatable shaft to limitthe shaft to rotation in one direction comprising the combination ofclaim 1 wherein the first hub is provided with a transverse lubricantpassageway above the gear of said first hub, said first hub defines alubricant entry communicating with said transverse lubricant passageway,a source of liquid lubricant connected to said lubricant entry in saidfirst hub, and an outlet port in said transverse passageway, said outletport being positioned above and confronting the gear of said first huband the upper gear of the sleeve so that lubricant falls from said porton the meshed gears of the first hub and sleeve.
 3. A one-way backstopfor engaging a rotatable shaft to limit the shaft to rotation in onedirection comprising the combination of claim 1 wherein the sleeve isprovided with a flat generally horizontal plate extending within theinner wall thereof between the gears thereof, said plate carrying aprotruding part-spherical button disposed on the lower side thereof andconcentric with the central axis of the first hub, said button restingon a generally horizontal surface on the second hub, and said horizontalplate having an aperture confronting said horizontal surface on thesecond hub so that lubricant from the gears of the first hub collectingon the generally horizontal plate flows through the aperture thereof toflood the flat surface on the second hub and lubricate the button andflat surface of the second hub.
 4. A one-way backstop for engaging arotatable shaft to limit the shaft to rotation in one directioncomprising the combination of claim 1 wherein the cup-shaped collectoris disposed above the region of the one-way torque coupling between saidinner and outer races thereof, whereby liquid lubricant overflowing theupper edge of the cylindrical wall of said collector drips on theone-way torque coupling.
 5. A one-way, self-alining torque unitcomprising, in combination, a generally circular upper coupler havingone face adapted for attachment to a stationaRy support, said uppercoupler having a gear support on the underside thereof, an upperexternal gear fixed to said gear support and defining an annular seriesof radially projecting crowned gear teeth, a lower coupler disposed inunderlying generally coaxial relation to said upper coupler, a lowerexternal gear fixed to said lower coupler and defining an annular seriesof radially projecting crowned gear teeth, a connecting coupler sleeveaxially spanning said upper and lower gears in encircling relationthereto, said sleeve having an upper internal gear and a lower internalgear meshing respectively with said upper and lower external gears totransmit torque therebetween while allowing movement of said lowercoupler and said lower external gear thereon in relation to said uppercoupler, said upper coupler having thereon a lubricant fountainpositioned in overlying relation to said upper external gear and saidupper internal gear to direct lubricant downwardly thereonto, a sleevesupport disc medially positioned axially on said coupler sleeve andextending transversely thereacross in overlying relation to said lowercoupler, said support disc defining on the underside thereof a convexthrust element supported on the upper end of said lower coupler, saidsupport disc having an aperture medially located therein to directlubricant through the support disc onto said lower coupler adjacent saidthrust element to lubricate the latter and to flow over said lowercoupler onto said lower external gear and said lower internal gear tolubricate the latter, a lubricant retaining cup mounted on said lowercoupler in encircling relation to the latter below said internal andexternal lower gears and extending upwardly in encircling spacedrelation to the lower portion of said sleeve to retain lubricant inpooling relation to said lower gears, a first one-way torque couplingrace disposed below said cup and fixed to said lower coupler, a secondone-way torque coupling race disposed in encircling relation to saidfirst race for rotation relative thereto, a roller cage assemblydisposed between said races in coacting relation thereto to transmittorque therebetween in only one rotary direction to preclude rotation ofthe races relative to each other in said one direction while permittingfree relative rotation of the races in the opposite direction, saidraces and said roller cage assembly being positioned to receivelubricant overflowing said lubricant cup, a sleeve bearing supportedwithin said first race in coaxial relation to said lower gear, a spindleconnected with said second race and journalled within said sleevebearing to maintain said races in mutually coaxial relation, means forconnecting said second race nonrotatably with a rotary part, lubricantsupply means connected with said lower coupler for supplying lubricantthereto, and a lubricant fountain connected to receive lubricant fromsaid lower coupler and positioned to pour lubricant onto the cageassembly intervening between said races.
 6. A one-way, self-aliningtorque unit comprising, in combination, an upper coupler adapted tosustain a torque reaction, an upper external gear fixed to said uppercoupler, a lower coupler disposed in underlying generally coaxialrelation to said upper coupler, a lower external gear fixed to saidlower coupler, a connecting coupler sleeve axially spanning said upperand lower gears in encircling relation thereto, said sleeve having anupper internal gear and a lower internal gear meshing respectively withsaid upper and lower external gears to transmit torque therebetweenwhile allowing movement of said lower coupler and said lower externalgear thereon in relation to said upper coupler, a lubricant outletpositioned to flow lubricant onto said upper external and internalgears, a sleeve support element supporting said coupler sleeve on saidlower coupler, a lubricant retaining cup mounted on said lower couplerin encircling relation to the latter below said internal and externallower gears anD extending upwardly in encircling spaced relation to thelower portion of said sleeve to retain lubricant in pooling relation tosaid lower gears, a first one-way torque coupling race of annular formdefining a circumferential series of roller support surfaces slopingoutwardly in a common circumferential direction; said lower couplerincluding means for supporting said annular race thereon below said cupin generally coaxial relation to said gears in either of two mountingpositions, which positions are turned end for end in relation to eachother so that the common slope of said roller supporting surfaces isselectively oriented circumferentially in either of two circumferentialdirections; a second one-way coupling race encircling said first race,an annular series of rollers disposed between said races in alinementwith said respective surfaces to transmit torque between the races inonly one direction predetermined by the selected orientation in whichsaid inner race is assembled onto said lower coupler thereby precludingrelative rotation of said races in said one direction while continuouslypermitting relative rotation of the races in the opposite direction,said races and said rollers being positioned to receive lubricantoverflowing said cup, means for connecting said second race nonrotatablywith a rotary part, and a lubricant fountain positioned to flowlubricant into the space intervening between said races.
 7. A one-way,self-alining torque unit comprising, in combination, an upper coupleradapted to sustain a torque reaction, an upper external gear fixed tosaid upper coupler, a lower coupler disposed in underlying generallycoaxial relation to said upper coupler, a lower external gear fixed tosaid lower coupler, a connecting coupler axially spanning said upper andlower external gears in encircling relation thereto, said connectingcoupler having an upper internal gear and a lower internal gear meshingrespectively with said upper and lower external gears to transmit torquetherebetween while allowing movement of said lower coupler and saidlower external gear thereon in relation to said upper coupler, alubricant outlet positioned to flow lubricant onto said gears, a firstone-way torque coupling race of annular form defining a circumferentialseries of roller support surfaces sloping outwardly in a commoncircumferential direction; said lower coupler including means forsupporting said annular race thereon in generally coaxial relation tosaid gears in either of two mounting positions, which positions areturned end for end in relation to each other so that the common slope ofsaid roller supporting surfaces is selectively orientedcircumferentially in either of two circumferential directions; a secondone-way coupling race encircling said first race, an annular series ofrollers disposed between said races in alinement with said respectivesurfaces to transmit torque between the races in only one directionpredetermined by the selected orientation in which said inner race isassembled onto said lower coupler thereby precluding relative rotationof said races in said one direction while continuously permittingrelative rotation of the races in the opposite direction, means forconnecting said second race nonrotatably with a rotary part, and alubricant outlet positioned to flow lubricant into the space interveningbetween said races.
 8. A one-way, self-alining torque unit comprising,in combination, an upper coupler adapted to sustain a torque reaction, afirst annular series of torque transmitting teeth on said upper coupler,a lower coupler disposed below said upper coupler, a second annularseries of torque transmitting teeth on said lower coupler, a connectingcoupler of generally cylindrical overall form extending axially intoaxially overlapping relation to said first and second series of teeth onsaid upper and lower couplers respectively, said connecting couplerhaving an upper annular series of torque transmitting teeth and a loweraNnular series of torque transmitting teeth meshing respectively withsaid first and second annular series of teeth to transmit torque betweensaid upper and lower couplers while allowing movement of said lowercoupler nonrotatably in relation to said upper coupler, an oil collectorcup mounted on said lower coupler in encircling relation to the latterbelow said connecting coupler and extending upwardly in encirclingrelation to the connecting coupler to retain an annular pool of oil inimmersing relation to torque transmitting teeth on the connectingcoupler and coupler teeth meshing therewith, lubricating means includinga lubricant outlet positioned to direct a flow of oil onto meshingtorque transmitting teeth of the aforementioned couplers and into saidoil collector cup to form a pool of oil therein, a first one-way torquecoupling race of generally circular form disposed below said cup andfixed to said lower coupler, a second one-way torque coupling race ofgenerally circular form disposed in encircling relation to said firstrace for rotation relative thereto, one of said races defining anannular series of roller support surfaces sloping toward the other racein a common circumferential direction, an annular series of rollersdisposed between said races in alinement with said respective rollersupport surfaces to transmit torque between the races in only onedirection to preclude rotation of the races relative to each other insaid one direction while permitting free relative rotation of the racesin the opposite direction, a sleeve bearing supported within said secondcoupler in coaxial relation to said first race, a spindle connected withsaid second race and journalled within said bearing to maintain saidraces in mutually coaxial relation, means for connecting said secondrace nonrotatably with a rotary part, lubricating oil supply meansconnected with said lower coupler for supplying lubricating oil thereto,and means on said lower coupler defining a lubricating oil passage fordirecting lubricating oil from said lower coupler onto said rollersintervening between said races.
 9. A torque unit according to claim 8 inwhich said connecting coupler is floatingly supported by a plurality ofsprings disposed within said oil collector cup.
 10. A torque unitaccording to claim 8 in which said first annular series of torquetransmitting teeth on said upper coupler are internal teeth meshing withexternal teeth constituting said upper annular series of torquetransmitting teeth on said connecting coupler and said second annularseries of torque transmitting teeth on said lower coupler are externalteeth meshing with internal teeth constituting said lower annular seriesof torque transmitting teeth on said connecting coupler.
 11. A torqueunit according to claim 10 in which said second annular series of torquetransmitting teeth are formed on the lower end portion of a generallycylindrical hub extending upwardly along said lower coupler inencircling relation thereto for an axial distance which is several timesgreater than the axial extent of the mutually overlapping relation ofsaid second series of teeth on said lower coupler with said lower seriesof teeth on the connecting coupler, a key is recessed into said hub andsaid second coupler in axially extending relation thereto to hold thehub and the second coupler against rotation relative to each other, andsaid first annular series of torque transmitting teeth and said upperseries of teeth on the connecting coupler are located substantially inencircling relation to the upper end portion of said hub.
 12. A torqueunit according to claim 11 in which said oil collector cup extendsupwardly into overlapping encircling relation to the mutually meshingteeth of said first series and of said upper series on the connectingcoupler to hold an annular pool of oil in immersing relation thereto.